Metal forming machine



Nov. 9, 1965 E. o. ACKER METAL FORMING MACHINE 4 Sheets-Sheet 1 Filed March 15, 1965 S m Q Ma T K N N C Du w m lf i w w m mfl gflm fi m mm an W Y kw B 1 m 2 mm m 9 3 Nov. 9, 1965 E. o. ACKER METAL FORMING MACHINE 4 Sheets-Sheet 2 Filed March 15, 1965 INVENTOR.

ERIC 0. ACKER kw 2W Q; W

ATTORNEYS Nov. 9, 1965 Filed March 15, 1965 E. o. ACKER 3,216,083

METAL FORMING MACHINE 4 Sheets-Sheet 4 III,

I I mug 11 a INVENTOR. 59/6 00 Aczr-e United States Patent 3,216,083 METAL FORMING MACHINE Eric 0. Acker, 4436 NW. 59th St, Oklahoma City, Okla. Filed Mar. 15, 1965, Ser. No. 453,236 8 Claims. (Cl. 296.2)

This is a continuation-in-part of application, Serial No. 139,798, filed September 21, 1961, and now abandoned.

This invention relates generally to improvements in metal forming machines, and more particularly, but not by way of limitation, to an improved machine for forming expanded metal from a metal plate.

As it is well known in the art, an expanded metal machine utilizes a pair of mating dies alternately engaged and disengaged, with one of the dies being shifted or indexed relative to the other die each time the dies are disengaged, in order to produce the desired form in the resulting expanded metal product. The sheet metal being formed into expanded metal is moved a predetermined distance through the opening between the dies each time the dies are disengaged. The mechanisms required for operating the dies and moving the sheet material through the machine must be structurally strong and yet have a high degree of precision in operation. Prior expanded metal machines have experienced substantial difficulty in both of these requirements, and particularly the degree of precision required. For example, one type of prior machine utilizes a spring loaded, lost motion assembly for shifting or indexing one of the dies in opposite directions when the dies are disengaged. This type of mechanism does not provide the required precision and is extremely difiicult and time consuming to adjust or change when a different type of expanded metal product is to be made by the machine.

Prior machines have also experienced difficulty in maintaining precision with regard to the extent to which the material being worked upon is moved or indexed between the stamping or forming operations. Furthermore, prior machines have not effectively prevented tilting or canting of the movable die which is caused by the dies engaging the metal being worked upon at an angle with a great force. In an expanded metal machine, the dies provide a shearing type action on the sheet metal and large forces are imposed on the dies; particularly the movable die, tending to cause the die to tilt, or cant, when brought into contact with the metal being formed.

The present invention contemplates a metal forming machine utilizing a movable and a stationary die wherein the movable die is indexed or shifted by a positively acting lever and cam system precisely operated in timed relation to the opening and closing movements of the dies. The present machine also utilizes a simply constructed adjusting mechanism for precisely adjusting and controlling the degree of indexing of the movable die in a minimum of time and with a minimum of effort on the part of the operator of the machine. The sheet metal to be worked on is fed through the machine by a pair of feed rollers precisely timed and controlled with respect to the opening and closing movements of the dies. One of the feed rollers is an idler and the other feed roller is operated by means of a one-way clutch assembly which positively prohibits any backlash of the feed roller system, and feeding movement of the feed rollers is precisely controlled by a cam system. The present machine also utilizes a simply constructed bracing system for preventing tilting, or canting, of the movable die without interfering with the indexing movement of the movable die. This bracing system includes a series of rollers in contact with the movable die supporting member to minimize interference with indexing of the movable die and yet allow easy and efficient replacement 3,215,083 Patented Nov. 9, 1965 of dies when different forms of expanded metal are being made with the same machine.

An important object of this invention is to provide a structurally strong metal forming machine having a high degree of precision in operation.

Another object of this invention is to provide a lever and cam system for positively indexing the movable die of a metal forming machine.

Another object of this invention is to facilitate the adjustment or changing of the indexing movement of a metal forming machine movable die.

A further object of this invention is to precisely control the feeding of sheet material through an expanded metal forming machine.

Another object of this invention is to eliminate tilting or canting of the movable die of a metal forming machine.

A still further object of this invention is to provide a metal forming machine whichis simple in construction, may be economically manufactured and which will have a long service life.

Other objects and advantages of the invention will be evident from the following detailed description when read in conjunction with the accompanying drawings which illustrate my invention.

In the drawings:

FIG. 1 is a side elevational view of a metal forming machine constructed in accordance with this invention with portions of the structure broken away to illustrate details of construction.

FIG. 2 is an enlarged partial vertical cross-sectional view taken along lines 2-2 of FIG. 1.

FIG. 3 is an enlarged detailed view of a portion of the righthand end of the machine illustrated in FIG. 1 illustrating a portion of an indexing system for the movable die.

FIG. 4 is an enlarged detailed view of a portion of the lefthand end of the machine shown in FIG. 1 illustrating another portion of the indexing system for the movable die.

FIG. 5 is an end view of the righthand end of the machine shown in FIG. 1.

FIG. 6 is a cross-sectional view taken along lines 6-6 of FIG. 5 with the driving chain for the indexing system removed for clarity of illustration.

FIG. 7 is an enlarged elevational view of the mechanism for adjusting the extent of indexing of the movable die.

FIG. 8 is a cross-sectional view as taken along lines 8-8 of FIG. 7.

FIG. 9 is a sectional view through the main drive shaft of the machine taken in a plane extending normal to the axis of the drive shaft and parallel and adjacent to one of the movable die actuating cams and illustrating the cam configuration.

FIG. 10 is an enlarged cross-sectional view of an indexing or one-way clutch taken along the lines 1010 of FIG. 5.

FIG. 11 is a cross-sectional view of the indexing clutch taken along the lines 1111 of FIG. 10.

FIG. 12 is an enlarged view of a portion of FIG. 11 illustrating the parts of the indexing clutch in one operational position.

FIG. 13 is a view similar to FIG. 12, but illustrating the parts of the indexing clutch in another operational position.

Referring to the drawing in detail, and particularly FIG. 1, reference character 10 generally designates a metal forming machine constructed in accordance with this invention and which includes a suitable power unit 12 positioned at one end of the machine. The vpower unit 12 may be of any desired construction and utilize any desired driving mechanism, such as an electric motor, and is therefore not shown in detail herein.

The main frame 14 of the machine may be formed as a single large casting and is provided with vertically extending end plates 16 and 18 at the opposite ends thereof. Flanges 20 extend outwardly from the end plates 16 and 18 to provide covers for the drive and indexing systems of the machine, which will be described below. The end plates 16 and 18 are interconnected by an arcuate section 22 at the top of the machine which provides protection for part of the operating portions of the machine and enhances the overall appearance of the machine. A cross member 24 is also positioned at the lower end of the machine to interconnect the end plates 16 and 18.

The main drive shaft 26 of the machine 10 extends lengthwise through the upper portion of the machine between the end plates 16 and 18 and is extended through the end plate 16 to receive a pulley or the like 28. A belt or the like 30 extends from the power unit 12 over the pulley 28 to turn the drive shaft 26 and operate the remainder of the machine, as will be described below.

The opposite end portions of the drive shaft 26 are journaled in suitable bearings 32 slidably supported for vertical movement by guides 34 which are preferably cast integrally with the frame 14. The bearings 32 and guides 34 are also illustrated in FIG. 6. Each bearing 32 is positioned by means of a screw 36 threaded through the upper portion 22 of the frame 14. Suitable handles 38 are provided on the upper end of each screw 36, and a locking nut assembly 40 is provided on each screw 36 in contact with the top portion 22 of the frame 14 to lock the screws 36 in the desired portions. Each screw 36 extends downwardly into contact with the upper end of the respective bearing 32 to adjust the height of the respective bearing 32 and hence the height of the respective end portion of the drive shaft 26. The drive shaft 26 is constantly urged upwardly, as will be described, such that the screws 36 can be adjusted to position the drive shaft 26 horizontally or tilted at any desired angle, depending upon the forming operation taking place.

A series of earns 42 are mounted in longitudinally spaced relation around the drive shaft 26 to provide reciprocation of a ram 44. Each cam 42 has a single lobe thereon as shown in FIG. 9 and all of the lobes of the earns 42 are aligned along the length of the drive shaft 26 to act in unison in forcing the ram 44 downwardly for a forming or expanding operation. It will also be noted that each cam 42 slides over a pad 46 mounted on top of the ram 44 to provide good bearing surfaces between the cams and the ram.

As shown in FIGS. 3, 4 and 5, a pair of plates 48 are secured to each end of the ram 44 and extend through a vertical slot 50 in the respective frame end plate 16 or 18. Each pair of plates 48 are extended vertically and are spaced apart a sufficient distance to slide along the opposite sides of the respective slot 50 to guide the ram 44 during the vertical reciprocating movements of the ram, as will be described. A block 52 is secured to the lower ends of each pair of plates 48, and a mating block 54 (FIG. 5) is provided on the respective end plate 16 or 18 below the slot 50. A plurality of compression springs 56 are anchored between each pair of blocks 52 and 54 to resiliently support the opposite ends of the ram 44 and constantly urge the ram upwardly. Each spring 56 is provided with a rod guide 58 extending therethrough to maintain the springs in the desired operating positions. Thus, the drive shaft 26 moves the ram 44 downwardly through the medium of the earns 42 and support pads 46 once each revolution of the drive shaft, and the springs 56 return the ram 44 upwardly to maintain the ram in constant sliding contact with the cams 42.

As shown in FIG. 2, the ram 44 is substantially rectangular in vertical cross-section and is disposed above a stationary bed 60, with the side 62 of the ram adjacent the bed 60 being offset or spaced horizontally from the adjacent side 64 of the bed 60. The bed 60 is suitably secured in a fixed position on the frame 14 of the machine 10 and extends horizontally along the length of the frame 14 between the end plates 16 and 18. A groove 65 is formed in the face 62 of the ram 44 at the lower end of the ram and along the length of the ram to provide a flat shoulder or surafce 66 facing in the direction of the bed 60 and a downwardly facing shoulder 68. A shuttle bar 70 is positioned to slide on the shoulders 66 and 68 lengthwise along the ram 44 and is held in sliding engagement with these shoulders by bolts 72 which extend through elongated slots 74 (FIGS. 3 and 4) formed through the shuttle bar. Thus, the shuttle bar 70 is held in the desired vertical position against the shoulders 66 and 68 but yet can slide lengthwise with respect to the ram 44.

A die 76 is suitably secured to the lower end of the shuttle bar 70, such as by bolts (not shown), and a mating die 78 is secured to the upper end of the stationary bed 60. The movable die 76 is secured in a groove 80 in the lower end of the shuttle bar 70 to transfer all forces imposed on the die 76 through the shuttle bar. The lower stationary die 78 is secured in a mating groove 79 in the bed 60 and is held in a rigid position by a plurality of bolts 82.

The mating dies 76 and 78 may take any desired form depending upon the shape desired in the finished expanded metal product being formed from a sheet 84 of metal. In any event, substantial forces are imposed on both of the dies 76 and 78 when the movable die 76 is moved downwardly to engage the sheet metal 84. These forces are effectively taken care of in the stationary die 78 by the rigid coupling of this die to the bed 60 by the bolts 82. However, the forces imposed on the movable die 76 tend to tilt or cant the die 76 and the corresponding shuttle bar 70 in a direction to move the shuttle bar 70 away from the face 66 of the ram 44. To counteract this tilting force, I provide a plurality of bracing members generally designated by reference character 86.

Each bracing member 86 comprises a structurally strong bracket 88 secured to the face 62 of the ram 44 by a pair of bolts 90 directly above the slot receiving the shuttle bar 70. Each bracket 88 extends downwardly and is provided with a slot 92 therein facing the respective side of the shuttle bar 70. A yoke 94 is slidingly disposed in each slot 92 and is provided with a roller 96 journaled in the free ends thereof, with the roller 96 being supported to rotate about a vertical axis. An adjusting screw 98 is threaded through the bracket 88 into contact with the yoke 94 for forcing the respective roller 96 into contact with the adjacent face of the shuttle bar '70 and urge the shuttle bar 70 against the face 66 of the ram 44. Thus, forces tending to tilt the movable die 76 and shuttle-bar 70 are effectively counteracted through the roller 96, yoke 94, and bracket 88. It will also be noted that the roller 96 provides a minimum restriction to the lengthwise indexing movement of the shuttle bar 70 which is provided by another mechanism to be described. The adjusting screw 98 may be easily retracted to retract the roller 96 from the shuttle bar 70 when the dies are to be changed, to greatly facilitate this operation. As illustrated in FIG. 1, I prefer to provide four of the brackets 86 along the length of the ram 44 in a machine of substantial size to effectively prevent tilting or canting movement of the movable die.

As previously indicated, the shuttle bar 70 and movable die 76 are reciprocated or indexed lengthwise on the ram 44 during operation of the machine 10. This indexing movement is controlled by a cam and lever system to precisely control the extent of indexing and the timing of indexing with respect to the vertical reciprocating movements of the ram 44. As shown in FIGS. 5 and 6, the end portion 100 of the main drive shaft 26 opposite the end of the drive shaft having the pulley 28 thereon, is reduced in diameter and extended through the respective frame end plate 18. A sprocket 102 is mounted on the shaft portion 100 to drive an endless chain 104. The chain 104 extends over a sprocket 106 mounted on a first cam shaft 108; a sprocket 110 mounted on a second cam shaft 112, and an idler sprocket 114. It will be apparent that the idler sprocket 114 is secured to the frame end plate 18 by an arm 116 in order that the position of the sprocket 114 can be varied to control the tension imposed on the chain 104. It will also be apparent that, upon rotation of the main drive shaft 26, the sprocket 102 will drive the cam shafts 108 and 112 through the medium of the endless chain 104 and the sprockets 106 and 110 in timed relation to the rotation of the main drive shaft.

The first cam shaft 108 is journaled in the frame end plate 18 and an arm 118 secured to the frame 14 to rotatably support the cam shaft 108 parallel with the main drive shaft 26. A cam 120 is rigidly secured on the cam shaft 108 and is provided with a tapered outer face 122 for controlling the movement of a follower 124. It will be noted that the sprocket 106 on the cam shaft 108 is of a size with respect to the sprocket 102 on the drive shaft 26 to rotate the cam 120 once for each two revolutions of the main drive shaft and the tapered face 122 of the cam 120 is tapered outwardly from the center of the cam to the outer edge of the cam around a portion of the circumference of the cam to force the cam follower 124 outwardly with respect to the frame end plate 18 during a limited portion of each revolution of the cam 120. Thus, the follower 124 is moved outwardly for a limited period of time during each revolution of the cam 120 and is in a retracted position during the remaining portion of the respective revolution of the cam 120. It will be understood that the cam surface 122 is sloped gradually to provide a smooth reciprocating movement to the follower 124. However, since the cam surface 122 is tapered outwardly from the central portion of the cam, the follower 124 will be moved outwardly a distance depending upon the radial position of the follower with respect to the cam 120. That is, when the follower 124 is near the outer edge or circumference of the cam 120, the follower will be moved further from the end plate 18 than it is when the follower is near the central portion of the cam. Thus, the extent of movement of the follower 124 is controlled by the relative position of the follower with respect to the cam 120. This positioning of the follower 124 is controlled by the construction of the follower which is illustrated in FIGS. 7 and 8.

The follower 124 comprises a housing 126 having an elongated slot 128 in the side thereof facing the cam 120. The housing 126 is supported on one end of a lever 130 (FIG. 6) in such a manner that the slot 128 extends radially with respect to the cam 120. A threaded indexing shaft 132 is suitably journaled in the opposite ends of the housing 126 and has a control knob 134 on one end thereof to control the setting of the shaft. A yoke 136 is constructed to slide along the housing 126 and has a shank portion 138 extending through the slot 128 into sliding contact with the walls of the slot 128. The indexing shaft 132 is threaded through the shank 138, such that the yoke 136 will be moved along the slot 128 and the housing 126 upon turning of the shaft 132. A suitable roller 140 is journaled in the yoke 136 in a direction to make rolling contact with the tapered face 122 of the cam 120 during rotation of the cam. Thus, when the extent of movement of the cam follower 124 is desired to be increased, the knob 134 is turned in a direction to move the yoke 136 and the roller 140 nearer the outer circumference of the cam 120, and vice versa.

The lever 130 (FIGS. 5 and 6) is pivotally supported for movement of the follower 124 toward and away from the frame end plate 18 by a shaft 142 extending through the central portion of the lever from brackets 144 mounted on the frame end plate 18. The end 146 of the lever opposite the end having the follower 124 is provided with a push rod 148 (FIG. 3) extending toward the respective end of the shuttle bar 70. It will also be noted that the outer end of the push rod 148 is rounded for sliding contact with the vertically extending fiat face 150 of a head 152. The head 152 is mounted on a rod 154 extending from the respective end of the shuttle bar 70 between the guide plates 48 of the ram 44 to position the head 152 outwardly of the supporting structure for the ram 44. The face 150 of the head 152 is of a size to provide contact with the push rod 148 in all positions of the shuttle bar 70 and ram 44. In other words, since the ram 44 and shuttle bar 70 are reciprocated vertically during operation of the machine, the face 150 of the head 152 must be of a size to maintain contact with the push rod 148 during this reciprocating movement. The push rod 148 stays at substantially the same level during operation of the machine. It will be apparent that, when the lever 130 is pivoted by outward movement of the cam follower 124, the push rod 148 is forced against the face 150 to urge the head 152, rod 154, and shuttle bar 70 in the direction of the opposite frame end plate 16. Since the shuttle bar 70 is mounted on the ram 44 by means of the bolts 72 and slots 74, the shuttle bar is free to move lengthwise to a limited extent.

Return movement or indexing of the shuttle bar 70 and the movable die 76 is provided :by a spring 156 provided at the opposite end of the machine from the lever 130. As shown in FIG. 4, the spring 156 is anchored between a plate 148 rigidly secured to the respective guide plates 48 and the respective end of the shuttle bar 70 to constantly urge the shuttle bar 70 toward the frame end plate 18. Also, a suitable guide rod 160- is preferably extended through spring 156 to maintain the spring 156 in the desired position. Thus, when the head 152 is released by the push rod 148 (by reason of the follower 124 being in contact with the flatter portion of the cam 120) the spring 156 moves the shuttle bar 70 and die 76 back toward the frame end plate 18. As previously indicated, the follower 124 is moved outwardly once each revolution of the cam 1.20. Thus, the push rod 148 moves the shuttle bar 70 and die 76 toward the end plate 16 for a limited portion of each revolution of the cam 120, and the spring 156 moves the shuttle bar 70 and die 76 back toward the end plate 18 as soon as the head 152 is released by the push rod 148. As also previously indicated, the cam 120 is turned once for each revolution of the main drive shaft 26, such that the movable die 76 will be indexed into its alternate positions once for each two vertical reciprocating movements of the die. The relative positions of the cam 120 with respect to the cams 42 on the main drive shaft 26 is such that the movable die 76 is in its position nearest the end plate 18 when the ram 44 is moved downwardly to engage the mating die 78; is shifted toward the end plate 16 when the ram 44 is raised; is held nearest the end plate 16 during the next downward movement of the ram 44; and is then indexed back to the position nearest the end plate 18 when the ram 44 is next raised, etc.

The second cam shaft 112 is also journaled in the end plate 18 and an arm 162 extending from the frame 14 in a position parallel with the main drive shaft 26. The cam shaft 112 is utilized for operating through a one way clutch (later described), a feed roller 164 extending along the length of the machine 10 between the end plates 16 and 18 in front of the stationary bed 60 as illustrated in FIGS. 1 and 6. The feed roller 164 cooperates with an idler roller 166 in feeding the material 84 over the bed 60, as will be described. A cam 168 (FIG. 6) is rigidly secured on the cam shaft 112 and has a tapered outer surface 170 arranged eccentrically with respect to the cam shaft 112. A second cam follower 172 is supported on the upper end 173 of a second lever 174 (FIG. in sliding contact with the tapered surface 170 of the cam 168 to pivot the lever 174 in accordance with the position of the cam. The follower 172 is mounted on an adjusting screw 176 extending through the upper end 173 of the lever 174 to adjust the position of the follower 172 with respect to the tapered surface 170 of the cam 168. It will be observed in FIGS. 5 and 6 that the tapered surface 170 of the eccentric portion of the cam 168 is tapered outwardly toward the end plate 18, such that the extent of movement of the lever 174 will be increased as the follower 172 is moved toward the end plate 18.

The lever 174 is pivotally supported at its central portion by a bracket 178 extending from the end plate 18. A roller 180 is provided on the lower end of the lever 174 to contact an upwardly extending lever 182 forming a part of a suitable one-way clutch assembly 184. The clutch assembly 184 is a commercially available device that may be obtained from the Formsprag Company of Warren, Michigan.

As shown in FIG. 10, one end of the feed roller 164 extends through the end plate 18 and is journaled therein by one or more bearings 186. A cylindrical inner race 188 is connected to the end of the feed roller 164 extending through the end plate 18 by one or more set screws 190. An outer race 192 having a sleeve bearing 194 therein encircles the exterior of the inner race 188 and is freely rotatable thereon. The outer race 192 has an enlarged bore 196 sized to receive a plurality of sprag members 198.

The lever 182 is attached to the outer race 192 by one or more set screws 193.

A clutch cover plate 200 encircles the inner race 188 and is sized to cover the bore 196 to prevent deleterious materials from entering the bore 196. A pair of spaced lock rings 202 and 204 are disposed in recesses 206 and 208, respectively, formed in the inner race 188 to position the outer race 192 and the cover plate 200 on the inner race 188.

As can be seen in FIG. 11, the sprags 198 are provided with a pair of spaced recesses 210 sized to receive a pair of annular energizing springs 212 for purposes that will be described more fully hereinafter. As shown in FIG. 11, the sprags 198 have a length that is greater than the distance between the outer surface of the inner race 188 and the bore 196 in the outer race 192. The annular energizing springs 212, disposed in the recesses 210 in the sprags 198, serve to hold the ends of the sprags 198 in contact with the inner race 188 and outer race 192.

As may be seen most clearly in FIG. 12, the sprags 198 are disposed at an angle relative to a radian R extending through the center of the roller 164. When the outer race is rotating in a clockwise direction, as shown by the arrow in FIG. 12, the outer race 192 moves relative to the inner race 188 because of the angle at which the sprags 198 are disposed.

However, when the outer ra'ce 192 is moved in the direction of the arrow shown in FIG. 13, the frictional engagement of the ends of the sprags 198 with the inner and outer races 188 and 192 tends to rotate the sprags 198 relative to the radian R and into tighter frictional engagement with the inner and outer races 188 and 192. Stated in another way, the sprags 198 are moved into a wedgin'g position wherein the inner and outer races 188 and 192 are caused to rotate together. The energizing springs 212 constantly bias the sprags 198 into frictional engagement with the inner and outer races 198 and 188 so that a very slight movement of the outer race 192 in the direction indicated by the arrow in FIG. 13 results in an instantaneous locking of the inner and outer races 188 and 192 preventing relative movement therebetween.

Thus, it can be seen that as the lever 174 rotates in a clockwise direction, as seen in FIG. 5, the lever 182 moves the outer race 192 in the direction of the arrow shown in FIG. 13 locking the clutch 184 and thereby transmitting a rotational movement to the inner race 188 and the roller 164 attached thereto. When the lever 174 moves in the counter-clockwise direction as seen in FIG. 5, the lever 182 is biased by a spring (not shown) so that it follows the cam roller on the lever 174, rotating the outer race 192 in the counter-clockwise direction shown by the arrow in FIG. 12 and relative to the inner race 188. As previously described, no rotational movement is transmitted to the race 188 or the attached roller 164 by the counterclockwise rotation of the outer race 192. Thus, it can be appreciated that the clutch 184 will transmit motion from the lever 174 to the roller 164 in one direction, but not in the other.

It will also be noted that the extent of movement of the lever 182, and hence the degree of rotation of the feed roller 164 is controlled by the extent of pivoting movement of the lever 174 by virtue of the position of the follower 172 with respect to the cam 168. further be noted that the lever 174 is pivoted once during each revolution of the cam 168, which, in turn, is rotated simultaneously with the main drive shaft 26. The timing of the rotation of the cam 168 with respect to the cam 42 on the main drive shaft 26 is such that the feed roller 164 is turned each time the ram 44 is raised to disengage the dies 76 and 78 to index or feed the material 84 a predetermined distance over the bed 60.

Operation In summarizing the operation of the machine 10, it will be noted that the power unit 12 'drives the main drive shaft 26 to reciprocate the ram 44 through use of the cams 42 and springs 56 atthe opposite ends of the ram. Each time the ram 44 is lowered, the mating dies 76 and 78 form the sheet metal 84 being fed over the bed 60 by the feed roller 164 and idler roller 166. Each time the ram 44 is raised to disengage the dies 76 and 78, the movable die is indexed lengthwise and the sheet metal 84 is indexed part way through the machine. The movable die 76 is indexed first in one direction and then in the other to provide the desired forming operation on the sheet metal 84 and produce an expanded metal product.

From the foregoing, it will be apparent that the present invention provides a structurally strong metal forming machine having a high degree of precision in operation. The movable die is indexed a precise distance in precisely timed sequence with the engaging and disengaging of the dies. The extent of indexing of the movable die and the sheet metal being fed through the machine are easily adjusted in a minimum of time. It will further be noted that the movable die is effectively supported against tilting without interference with the indexing movements thereof.

Changes may be made in the combination and arrangement of parts or elements described in the specification and shown in the drawings, it being understood that changes may be made in the precise embodiment disclosed without departing from the spirit and scope of the invention as defined in the following claims.

I claim:

1. A metal forming machine, comprising:

a frame;

a stationary bed mounted on the frame;

a ram slidably mounted on the frame for movement toward and away from the bed;

a shuttle bar slidingly carried by the ram for movement lengthwise along the ram;

mating dies secured on the shuttle bar and the bed;

drive means for reciprocating the ram toward and away from the bed for mating and, alternately, separating the dies; and,

means for shifting the shuttle bar and the respective die on the ram each time the dies are separated, said shifting means including a cam drivingly connected to said drive means for rotation of the cam in timed relation with re- It will ciprocation of the ram, said cam being circular in form and having a face thereof tapered outwardly in varying degrees from the central portion of the cam,

a follower in contact with the cam for following the contour of the cam, said follower including a housing extending radially with respect to the cam and having a slot in the wall thereof adjacent the tapered face of the cam,

a threaded index shaft journaled in the housa yoke extending through the slot in the housing and threaded onto the indexing shaft for movement lengthwise in the housing upon turning of the indexing shaft, and

a roller journaled in the yoke in rolling contact with the tapered face of the cam, whereby the extent of movement of the roller by the cam is adjusted by turning the indexing shaft, said movement occurring once each revolution of the cam,

a lever system extending from the follower to the shuttle bar for shifting the shuttle bar in one direction, and

spring means for shifting the shuttle bar in an opposite direction when the shuttle bar is released by the lever system.

2. A metal forming machine, comprising:

a frame having horizontally spaced vertical end plates;

a stationary bed on the frame extending horizontally between the frame end plates;

a ram slidingly supported by the frame end plates parallel with the bed for vertical movement toward and away from the bed;

a shuttle bar slidingly secured to the ram for reciprocating movement lengthwise on the ram;

mating dies secured on the bed and the shuttle bar;

a main drive shaft journaled to the frame above the ram and extending to the frame end plates parallel with the ram;

drive means for rotating the main drive shaft;

at least one cam on the main drive shaft in contact with the ram for urging the ram downwardly each revolution of the main drive shaft;

spring supports at the opposite ends of the ram urging the ram upwardly;

a cam shaft journaled in one frame end plate parallel with the main drive shaft;

a drive system for rotating the cam shaft simultaneously with rotation of the main drive shaft;

a cam follower;

a cam on the cam shaft engaging the follower and shaped to move the follower in a direction away from the adjacent frame end plate once each revolution of the cam;

a lever system connected to the follower for moving the shuttle bar in one direction when the follower is moved away from the adjacent frame end plate; and,

spring means for moving the shuttle bar in an opposite direction when the shuttle bar is released by the lever system.

3. A machine as defined in claim 2 wherein said lever system includes:

a lever pivotally supported from the frame end plate supporting the cam shaft;

one end of the lever being connected to the follower;

a push rod secured to the opposite end of the lever and positioned in the plane of movement of the shuttle bar; and,

a head carried by the shuttle bar in contact with the push rod and having a height as great as the vertical movement of the shuttle bar for maintaining contact between the head and push rod during all positions of the shuttle bar.

4. A metal forming machine, comprising:

a frame having horizontally spaced vertical end plates;

a stationary bed on the frame extending horizontally between the frame end plates;

a ram supported by the frame end plates parallel with the bed for vertical movement toward and away from the bed;

a shuttle bar slidingly secured to the ram for reciprocating movement lengthwise on the ram;

mating dies secured on the bed and the shuttle bar;

a main drive shaft journaled to the frame above the ram and extending to the frame end plates parallel with the ram;

drive means for rotating the main drive shaft;

at least one cam on the main drive shaft in contact with the ram for urging the ram downwardly each revolution of the main drive shaft;

spring supports at the opposite ends of the ram urging the ram upwardly;

a cam shaft journaled in one frame end plate parallel with the main drive shaft;

a drive system for rotating the cam shaft simultaneously with rotation of the main drive shaft;

a cam on the cam shaft being circular in form and having the face thereof remote from the adjacent frame end plate tapered outwardly in varying degrees from the central portion of the cam;

a cam follower including a housing extending radially with respect to the cam and having a slot in the wall thereof adjacent the tapered face of the cam,

a threaded index shaft journaled in the housing,

a yoke extending through the slot in the housing and threaded onto the indexing shaft for movement lengthwise in the housing upon turning of the indexing shaft, and

a roller journaled in the yoke in rolling contact with the tapered face of the cam, whereby the extent of movement of the roller by the cam is adjusted by turning the indexing shaft, said movement occurring once each revolution of the cam;

a lever system connected to the follower for moving the shuttle bar in one direction when the follower is moved away from the adjacent frame end plate; and,

spring means for moving the shuttle bar in an opposite direction when the shuttle bar is released by the lever system.

5. A machine as defined in claim 2 characterized further to include a pair of feed rollers journaled to the frame adjacent the bed for feeding material to be formed over the bed, and means connecting said drive system to one of the feed rollers for turning said one feed roller in timed relation to operation of the ram.

6. A machine as defined in claim 5 wherein said means for connecting said drive system to said one feed roller includes a one-way clutch assembly connected to said one feed roller for limiting turning movement of said one feed roller in only one direction.

7. A machine as defined in claim 6 wherein said means for connecting said drive system to said one feed roller further includes a lever pivotally supported by the adjacent frame end plate, one end of said lever being positioned to operate the one-way clutch, .a second cam shaft journaled to the frame and connected to said drive system, a second cam follower on the opposite end of said lever, and a second cam on the second cam shaft for actuating the second cam follower in timed relation to the movement of the ram.

8. A metal forming machine, comprising:

a frame having horizontally spaced vertical end plates;

a bed on the frame extending horizontally between the frame end plates;

a ram supported by the frame end plates parallel with the bed for vertical movement toward and away from the bed;

a shuttle bar slidingly secured to the ram for reciprocating movement lengthwise on the ram;

mating dies secured on the bed and the shuttle bar;

at least two brackets secured on the side of said ram;

a roller journaled in each bracket for rotation on a vertical axis in contact with said shuttle bar;

a main drive shaft journaled to the frame above the ram and extending to the frame end plates parallel with the ram;

drive mean-s for rotating the main drive shaft;

at least one cam on the main drive shaft in contact with the ram for urging the ram downwardly each revolution of the main drive shaft;

spring supports at the opposite ends of the ram urging the ram upwardly;

first and second cam shafts journaled in one frame end I plate parallel with the main drive shaft;

a drive system for rotating the cam shafts simultaneously with rotation of the main drive shaft;

a cam on the first cam shaft being circular in form and having the face thereof remote from the adjacent frame end plate tapered outwardly in varying degrees from the central portion of the cam;

a cam follower including a housing extending radially With respect to the cam and having a slot in the wall thereof adjacent the tapered face of the cam,

a threaded index shaft journaled in the housing,

a yoke extending through the slot in the housing and threaded onto the indexing shaft for movement lengthwise in the housing upon turning of the indexing shaft, and

a roller journaled in the yoke in rolling contact with the tapered face of the cam, whereby the extent of movement of the roller by the cam is adjusted by turning the indexing shaft, said movement occurring once each revolution of the cam;

a lever system connected to the follower for moving the shuttle bar in one direction when the follower is moved away from the adjacent frame end plates, said lever system including a lever .pivotally supported from the frame end plate, one end of the lever being connected to the follower, a push rod secured to the opposite end of the lever and positioned in the plane of movement of the shuttle bar;

a head carried by the shuttle bar in contact with the push rod and having a height as great as the vertical movement of the shuttle bar for maintaining contact between the head and push rod during all positions of the shuttle bar;

spring means for moving the shuttle bar in an opposite direction when the shuttle bar is released by the lever system;

a pair of feed rollers journaled to the frame adjacent the bed for feeding material to be formed to the bed; and,

means for driving one of said rollers including a cam on a said second cam shaft,

a lever pivotally mounted on the adjacent frame end plate,

a one-way clutch assembly connected to said driven roller,

a cam follower mounted on one end of said lever in contact with said second cam,

the arrangement being such that the opposite end of said lever actuates said one-way clutch upon movement of said follower whereby the material to be formed is fed in timed rotation to the movement of said ram.

No references cited.

RICHARD H. EANES, JR., Primary Examiner. 

8. A METAL FORMING MACHINE, COMPRISING: A FRAME HAVING HORIZONTALLY SPACED VERTICAL END PLATES; A BED ON THE FRAME EXTENDING HORIZONTALLY BETWEEN THE FRAME END PLATES; A RAM SUPPORTED BY THE FRAME END PLATES PARALLEL WITH THE BED FOR VERTICAL MOVEMENT TOWARD AND AWAY FROM THE BED; A SHUTTLE BAR SLIDINGLY SECURED TO THE RAM FOR RECIPROCATING MOVEMENT LENGTHWISE ON THE RAM; MATING DIES SECURED ON THE BED AND THE SHUTTLE BAR; AT LEAST TWO BRACKETS SECURED ON THE SIDE OF SAID RAM; A ROLLER JOURNALED IN EACH BRACKET FOR ROTATION ON A VERTICAL AXIS IN CONTACT WITH SAID SHUTTLE BAR; A MAIN DRIVE SHAFT JOURNALED TO THE FRAME ABOVE THE RAM AND EXTENDING TO THE FRAME END PLATES PARALLEL WITH THE RAM; DRIVE MEANS FOR ROTATING THE MAIN DRIVE SHAFT; AT LEAST ONE CAM ON THE MAIN DRIVE SHAFT IN CONTACT WITH THE RAM FOR URGING THE RAM DOWNWARDLY EACH REVOLUTION OF THE MAIN DRIVE SHAFT; SPRING SUPPORTS AT THE OPPOSITE ENDS OF THE RAM URGING THE RAM UPWARDLY; FIRST AND SECOND CAM SHAFTS JOURNALED IN ONE FRAME END PLATE PARALLEL WITH THE MAIN DRIVE SHAFT; A DRIVE SYSTEM FOR ROTATING THE CAM SHAFTS SIMULTANEOUSLY WITH ROTATION OF THE MAIN DRIVE SHAFT; A CAM ON THE FIRST CAM SHAFT BEING CIRCULAR IN FORM AND HAVING THE FACE THEREOF REMOTE FROM THE ADJACENT FRAME END PLATE TAPERED OUTWARDLY IN VARYING DEGREES FROM THE CENTRAL PORTION OF THE CAM; A CAM FOLLOWER INCLUDING A HOUSING EXTENDING RADIALLY WITH RESPECT TO THE CAM AND HAVING A SLOT IN THE WALL THEREOF ADJACENT THE TAPERED FACE OF THE CAM, A THREADED INDEX SHAFT JOURNALED IN THE HOUSING, A YOKE EXTENDING THROUGH THE SLOT IN THE HOUSING AND THREADED ONTO THE INDEXING SHAFT FOR MOVEMENT LENGTHWISE IN THE HOUSING UPON TURNING OF THE INDEXING SHAFT, AND A ROLLER JOURNALED IN THE YOKE IN ROLLING CONTACT WITH THE TAPERED FACE OF THE CAM, WHEREBY THE EXTEND OF MOVEMENT OF THE ROLLER BY THE CAM IS ADJUSTED BY TURNING THE INDEXING SHAFT, SAID MOVEMENT OCCURRING ONCE EACH REVOLUTION OF THE CAM; A LEVER SYSTEM CONNECTED TO THE FOLLOWER FOR MOVING THE SHUTTLE BAR IN ONE DIRECTION WHEN THE FOLLOWER IS MOVED AWAY FROM THE ADJACENT FRAME END PLATES, SAID LEVER SYSTEM INCLUDING A LEVER PIVOTALLY SUPPORTED FROM THE FRAME END PLATE, ONE END OF THE LEVER BEING CONNECTED TO THE FOLLOWER, A PUSH ROD SECURED TO THE OPPOSITE END OF THE LEVER AND POSITIONED IN THE PLANE OF MOVEMENT OF THE SHUTTLE BAR; A HEAD CARRIED BY THE SHUTTLE BAR IN CONTACT WITH THE PUSH ROD AND HAVING A HEIGHT AS GREAT AS THE VERTICAL MOVEMENT OF THE SHUTTLE BAR FOR MAINTAINING CONTACT BETWEEN THE HEAD AND PUSH ROD DURING ALL POSITIONS OF THE SHUTTLE BAR; SPRING MEANS FOR MOVING THE SHUTTLE BAR IN AN OPPOSITE DIRECTION WHEN THE SHUTTLE BAR IS RELEASED BY THE LEVER SYSTEM; A PAIR OF FEED ROLLERS JOURNALED TO THE FRAME ADJACENT THE BED FOR FEEDING MATERIAL TO BE FORMED TO THE BED; AND, MEANS FOR DRIVING ONE OF SAID ROLLERS INCLUDING A CAM ON A SAID SECOND CAM SHAFT, A LEVER PIVOTALLY MOUNTED ON THE ADJACENT FRAME END PLATE, A ONE-WAY CLUTCH ASSEMBLY CONNECTED TO SAID DRIVEN ROLLER, A CAM FOLLOWER MOUNTED ON ONE END OF SAID LEVER IN CONTACT WITH SAID SECOND CAM, THE ARRANGEMENT BEING SUCH THAT THE OPPOSITE END OF SAID LEVER ACTUATES SAID ONE-WAY CLUTCH UPON MOVEMENT OF SAID FOLLOWER WHEREBY THE MATERIAL TO BE FORMED IS FED IN TIMED ROTATION TO THE MOVEMENT OF SAID RAM. 